Gun control mechanism



Feb. 2l, 95@ H. ERNST ETAL 2,498,033

GUN CONTROL MECHANISM Filed No'v. 22, 1937 6 Sheets-Sheet l Jiffy 7Feb., 2E, 1950 H. ERNST ET AL 2,498,033

GUN CONTROL MECHANISM Filed Nov. 22 1937 6 Sheets-Sheei'l 2 i? Eg? ifFeb 2L i195@ H. ERNST ETAL GUN CONTROL MECHANISM 6 Sheets-Sheet 3 FiledNOV. 22, 1957 NNN Feb 2l, E95@ H. ERNST ETAL 2,498,033

GUN CONTROL MECHANISM Filed Nov. 22, 1937 6 Sheets-Sheet 4 Feb. 2l, E950H. ERNST ETAL. 2,498,033

GUN CONTROL MECHANISM Filed Nov. 22, 1937 6 Sheets-Sheet 5 Feb. 21, 1950H. ERNST ETAL 2,493,033

GUN CONTROL MECHANISM Filed Nov. 22, 1937 6 Sheets-Sheet 6 Parenteelrele. 21.1950 '2,498,033

UNITED STATES PATENT OFFICE GUN CONTROL MECHANISM Hans Ernst and BernardSassen, Cincinnati, Ohio, assignors, by mesne assignments, tothe United'States of America as represented by the Secre-` tary oi the NavyApplication November 22, 1937, Serial No. 175,830

8 Claims. (Cl. 89-41) 1 2 This invention relates toV motion transmittingFigure 7 isa section on the line 'l-'l of Figor signaling systems andmore particularly to ure 1. the type. wherein a follower is caused tomove Figure 8 is a section on the line 8--8 of Figin synchronism with atransmitter or director. ure 7.

One of the objects of this'invention is to pro- 5 Figure 9 is a'se'ctionthrough a transmitter vide an improved system which is highlysensitiveunit.

to any movement of the transmitter; which is Figure 10 is a section onthe. line Ill-I0 `oli positive in operation; and which is capablev orvFigure 9. p developing the necessary torque for effecting Figure 11 isa, section on the line ll-ll of movement of a receiver and alsomaintaining 10 Figure 10. the same in synchronous relation with thetrans.- Figure 12. is a section on the line I 2-K-l2 of mitter. Figurey6.

Another object of this invention is toA develop Figure, 13 is a sectionon the line |3--l3' of a system of the character mentioned which al-Figure 6.

though sensitive to a high degree, may be of 15 Figure 14 is a sectionvon the line Isl- I4 of rugged construction, thereby eliminatingdelicate Figure 6.

parts susceptive of easy breakage, or sensitive to Figure 15 is asection on the line I5-I5 of shocks causing maladjustment. thereof.Figure 6.

A further object of the invention is to provide Figure 16 is a sectionon the line lB-IG of a system as aforesaid in which hydraulic means 20Figure 6. may be utilized as the motion conveying or sig- Figure 1'7 isa diagram of' the hydraulic renaling medium, sistances.

An additional object of this invention is to Figure 18 is a diagrammaticView Showing the provide a system of the character mentioned relationbetween the change of resistance in the which may be compounded in sucha manner 25 transmitter elements relative to the change of thatmovement; in a plurality of planes may be resistance in the receiverelements.

placed under the control of a single element, This invention in itsbroad aspects, contemthereby providing a system whichA is; suitable forplates a signaling system forkthe transmission nre control purposes ofmilitary forces and espeof motion impulse signals from a transmitter tocially adapted for control of anti-aircraft defense 3f) a receiver in adefinite and positive manner, and so that one will always be insynchronism with weapons.

Other objects and advantages of. the present the other, whether at restor in motion. In the invention should be readily apparentA byreferattainmentof absolute synchronisma constantly vence to thefollowing specification, considered in acting force. must be everpresent so that even conjunction with the accompanying drawings u aftera. signal has been transmitted, the interillustrative of one embodiment,thereof, but it will connected parts will be held and maintained in beunderstood that any modifications may be their new positions therebypreventing Vinadmade in the specific structural detailswithin thevertent or accidental movement of the` receiver scope of the appendedclaims without departing out of synchronism with its transmitter ordifrom or exceeding the spirit of the invention. ,N rector. Morespeciiically, this invention contem` Referring to the drawings in whichlike4 referplates a signaling system in which yan hydraulic encenumerals indicate like or similar parts: medium isutilized fortransmittingl signals such Figure 1 is an elevation showing theapplicaas motion impulses, and which is so contrived tion of theinvention toanti-aircraft gun control. as. to provide aiirst group ofproperly related Figure 2 is a sectional View onthe line 2-2 ofpressural control elements in thev transmitter Figure 1. which actthrough individual hydraulic lanes to Figure 3 is a sectional view onthe line 3-3 of alter or unbalance the respective kpressures onFigure 1. v an equal. group 0f receiver actuators arranged Figure 4 is aview similar to Figure 2L showing to be effective as a couple to causemovement of a modified form of gearing between the transan ultimatereceiver element, which movement -m-itter and receiver. will continueuntil the actuators themselves by Figurev 5 is a view similar to-Figure3.showing theirown movementv cause reequalization of the a modied formof gearing. pressures acting upon them, and therebyV equil- .thereceivery motive power units.

Figure 6 is a longitudinal view through one of librium between theparts.. which not only stops the receiver elementbut holdslit in a givenposition. Accurate positioning is obtained because each increment ofmovement of the director causes a denite pressure differential on theactuators which will not be eliminated until the receiver actuators havemoved through that same increment.

Having effected a new position, the fluid pressure still acts but in anequalized manner so that even if the receiver actuators areinadvertently 01 accidentally disturbed, the fluid pressure will againbring them into synchronized relation with the respective controlelements. Such a system is thus admirably adapted forcontrolling, forinstance, the azimuth or elevation of a gun from a remote re controlstation and more particularly for` controlling the position ofanti-aircraft defense weapons. On account of the rapid movement ofaircraft, it is extremely difficult to follow their movements with theordinary gun sights because alignment ofthe sights with the target meansmovement of the gun, which is so-unwleld 1y as to prevent easy and fastmanual movement thereof. It is therefore desirable to use independent,easy and quickly movable sighting apparatus for this purpose. It isobvious that the movements of this apparatus must be immediatelytransmitted to the gun so that it will always be in a position to fireas soon as the target is properly located. In such a combination thesighting apparatus can be considered as the transmitter; and the gun asa receiver thus presenting an ideal condition for the application ofthis invention and it will therefore be described in connection with ananti-aircraft defense Weapon for control thereof. l

lThe relative position of Such a gun and its control mechanism may bethe same as that shown in Figure 1 inwhich the reference numeral Iindicates generally the gun, While the reference numeral II indicates ina general manner the control for the gun. Since aircraft in general arecapable of three ,directional movement as distinguished from the twodirectional movement of ordinary land or naval forces, it is necessarythat thev weapons used to combat aerial forces have a greater range ofadjustment than the ordinary land and naval weapons; and for thisreason, the gun barrel II is carried or mounted on a support I2 whichhas limited angular movement about a pivot I3 and in the plane of theupper surface I4 of a sub-support I5. This subsupport is mounted formovement about a pivot i I5 for elevational adjustment of the gun, thepivot being carried by a column or standard I1 which itself is angularlyadjustable in a horizontal plane about a pivot IB, the Weight of thestandard being transmitted through anti-friction bearings to a basemember 20. It will thus be seen that the gun may be adjusted in ahorizontal plane about the pivot I8; in a vertical plane about the pivotI6, and in an inclined plane about the pivot I3.v

The sighting apparatus must be capable of corresponding movement inthese various planes in order to properly control the gun by merelysighting the target, and for'this reason the director or sighting arm2I, carrying sights 22, at opposite ends thereof, is mounted formovement about a pivot 23, carried by a sub-support 24, mounted forangular movement in a vertial plane about the pivot 25. The pivot 25 iscarried by a vertical standard 26 which is mounted for rotation about apivot 21, its weight being transmitted to the base 28 throughanti-friction bearings 29. The director arm 2l may be moved throughmeans of the hand grasp 30, secured to one end thereof,

vinch as shown in 5S inFigure 11.

4 by the gunner or other operator, in a vertical plane, or for limitedmovement in any inclined plane about the pivot 23, 01 for completemovement through a circle about the pivot 21. Since the movement aboutthe pivot 21 is effected by a separate hand grasp 3I integral with themember 26, the movement about "the pivot 23v is provided so that smalladjusting movements may be made more quickly than if dependence wasplaced upon the control 3 I.

Mechanism has been provided whereby any movement of the sightingapparatus will be lmmediately communicated to the corresponding movableelements of the gun so that the axis of the gun will always be insynchronism with the axis passing through the sights 22. The sightingapparatus therefore constitutes a form of transmitter which is utilizedto signal the movements to be made in the gun, the system contemplatedby this invention effecting the gun movements automatically, andsimultaneously with the movement of the sighting apparatus.

A separate transmitter, such as shown at 32 in Figure 9, is operativelyconnected vwith each movable element so that the movement in therespective planes is transmitted by individual transmitters. Similarly,each of the movable parts of the gun support is provided with anindividual receiver which is Aof the same form as the transmitter 32shown in Figure 9, and this receiver is coupled for control of anhydraulic motive power unit for translating the signal received intopower movement of the gun. It should thus be obvious that the `threepossible planes of movement of the sighting apparatus have threeseparate transmitters which are connected to individual receivers in thegun, thereby constituting in effect three separate and distinctcommunication or signaling systems. Since all of the systems are thesame, only one will be described hereinybut it is to be remembered thateven although they function as separate entities they still may beprovided with uid pressure from a common source.

As shown in Figures 9, 10 and 11, the transmitter comprises a housing 33containing a cylinder block 34, in which is formed a plurality ofcylinders 35, 36, 31 and 3-8. Piston members 39, 40, 4I `and 42 aremounted in the respective cylinders 35, 36, 31 and 38 for movementtoward and from a common center member 43. Each piston has ananti-friction roller 44 journaled in the outer end thereof forcooperation with the inner contoured surface 45 of the manuallyrotatable member v46. The cylinder block 34, as more particularly shownin Figure 11, is interdrilled to provide a passage 41, to which thepressure channel 48 is connected when the device is used as atransmitter. When the device is used as a receiver a reservoir returnline is connected to this passage. The passage 41 is connected by fouraxially extending holes49, 50, 5l and 52 to separate angularly shapedpassages 53, 54, 55 and 56. These passages terminate in portsintersecting the respective cylinders, there being two ports on oppositesides of each cylinder so that the pressure serves to balancethe'pistons in the cylinders and prevent binding thereof. Each pistonhas a pair of grooves 51 formed on opposite sides thereof. Also, theportions of the periphery of the piston between the boundaries of thegrooves 51 are reduced in diameter by afew thousandths of an Adiametrical hole 59 in the piston interconnects the'grooves 51 with anaxial yhole 50 drilled in-oneend of each piston, these yaxial holesterminating at the space 6l existing at the inner end of each cylinder.The spaces 6l communicate with separate passages 62, 63, 64 and 65`formed in the center portion of the cylinder block and each in turn isconnected with a separate pipe extending to the receiver'. When thedevice shown in Figures and l1, is utilized as a transmitter, uid.pressure may be supplied, as by the channel 48, to the cylinder ports,through which it then passes to and through the narrow spaces 66, 61, 68and 69, which constitute hydraulic resistances, to the intersectingpassages 59 and '63, and from there through the spaces 6| to therespective channels 62, B3, 64 and 65. These .hydraulic resistances.cause a drop in .pressure between the lincoming fluid in channel v48and the outgoing iluid in channels 62, `63, 64 and `65. Also, thehydraulic resistances will cause a. dierent drop in 'pressure for eachpiston, depending upon the axial .position thereof in its cylinder, it-being apparent that when the piston 39, for instance, is at the limitof its outward stroke, the resistance will be at a maximum; while whenthe piston, such -as 4i, is at the end of its inward stroke theresistance will be at a predetermined shaped sur-faces lll, each ofwhich has the same contour and which are so formed that upon movementofthe member l446 through an arc lindicated by the reference numeral 1I,the piston will -bev moved inward through a complete stroke causing thehydraulic resistance to vary at a substantially uniform rate frommaximum to minimum, 'or from minimum to maximum "depending upon thedirection of rotation yof the cam 46. Upon unidirectional movement of`.the lmember 46, one half of the surface 7U may be considered as apiston advancing portion and ythe other-half as a piston retractingportion.

When `the device shownin Figures 10 .and 11 is utilized .fas 4areceiver, the direction of flow .through it will be reversed, the uidentering through channels 62,63, 64 `and 65 to act on the lends of thepistons and cause clockwise or -counter-clockwise rotation of the member46 and discharging through the hydraulic resistances in the variouspistons `to a return channel, which would be lsubstituted for `thechannel .48.

It -will thus beenseen that the system in its elementary form comprisesa source of fluid pres- -sure which isvconnected to a plurality ofparallel resistances which are simultaneously variable, .as

:by manual rotation of the member 46, in prede- Jtermined relation toone another, and a serially Aarranged equal number of resistances, whichare automatically variable in the same phase rela- 4tion so that denitepressures are created Ibetween the respective pairs of serialresistances,

:such yasin the channels 62, 63, 64 and 65and that the pressures inthese channels may be 'varied by changing the resistance at either rsidethereof.

In order to more clearly understand this relationship, a simple diagramhas been shown in Figure 17 in which the pressure supply line .isrepresented by the numeral 12; Vthe hydraulic resistances associatedwith pistons 39, 4U, 4|' and 42 by the respective resistance coils 13,14', 15 and 16 while the corresponding resistances in the receivermember are dagrammatically llustrated by the coils Tl, 18, 19 and 80,the respective pairs of resistances being interconnected by channels62', 63', 64' and 65 corresponding to channels 62, 63, 64 and 65 inFigure 10. The fluid escaping from the resistances 11 to 80 inclusivemay be connected in a common return line 8| and returned to a commonreservoir. Although the channel l2 has been indicated as a pressurechannel and the channel 8| as a return line, the functions of thesecould be reversed without changing the eiect or operation of thisdevice.

Although four lines have been shown in Figure 17,` a minimum .of threeparallel lines could bev used; but since `such an arrangement would notproduce uniform turning torque throughout the 3 60 degrees. of movementof the device, it .is preferable to use ya larger number although. theactual number used does not depart fr om the principles of thisinvention.

By using tour channels, it is. possible toarrange the pistons inOpposing pairs, or in other words, in couples, so that while one pair ispassing a dead center, the -other pair is active and capable `of'causing reverse rotation of vthe receiver.

It is a Well-known hydraulic principlethat the pressure P in a channelis a `function of the quantity-Q flowing through the channel, yand there-f sistance R in the .remainder of the channel be# tween thepoint-where the pressure is taken and the outlet; and this relationshipmay be expressed as n 'Figure 1'7 a portion of the various parallelbranch lines indicated as 53', 54", 55 and 56' correspond respectivelyto channels'53, 54', 55 and =56 'in Figure` 10. The pressure in each ofthese lines will be the same as the pressure inthe -mainsu-pply Aline'I2 and therefore in'accordance with the preceding equation, a vseparateequation may be written forr each parallel 'branch line. In these-equatio'nsQ Q2, Q3, and' 'Q4 represents the quantity olowintherespect'ive branch lines.

Alsoif tP1l=2,`1 3, andPrepresent the pressure in lthe respectivechannels 62" 63', 64' and 65.' `we may-writethe following equations: i

.Dividing Equations i5., 6,.'7 and 8 by Equations f1, 2, f3 and .4respectively, we have in simplified form:

ananas It will therefore be apparent that the respective pressures P1,P2, P3, P4 are each equal to one-half of the pressureA in the main line12. In other words if the resistance to ow in is equal to the resistanceto flow out of a given channel the pressure intermediate the resistancesis always equalv to one-half of the supply pressure. It should beremembered, however, that this does not means that because resistance 13is equal vto resistance 11, for instance, that the resistance 13 must beequal to the resistance 14 or resistance 15, or the resistance 16. Eachone of these four resistances may have different values but so long` asthe remaining serial resistance is equal to the first resistance, theintermediate pressure will be one-half of the supply pressure. It isthus possible to have the piston 39 at the end of its outward stroke,and the piston 4| at the end of its inward stroke, one presenting amaximum of resistance and the other a minimum resistance, and ystillhave the pressure at 62 and 64 in Figure 10 equal to one another.Similarly, the pressure at 63 and 65 may be equal to one another, andsince all four pressures are equal, no movement will result in therotatable member 46.

The change in resistance caused by any piston may be plotted against thelength of piston stroke as shown by the graph 62 in Figure 18 in whichthe distan-ce X represents the length of piston stroke and the distanceY represents the change in resistance from any predetermined minimum toany predetermined maximum. The orifices or ports and the surfaces 45 areso shaped that this changein resistance is substantially uniformthroughout the length of piston stroke. Also, since the length of pistonstroke corresponds to the movement of the member 46 through the arc 1|the length of piston stroke might also be .considered the length of.angular movement of the member 46 through the arc 1|. Therefore, areference line 83 has been drawn in Figure 18 and the graphs 84, 85 and86 positioned relative to this reference line in accordance with thephase relationship of pistons 4|, 40 and 42 respectively relative to thepiston 39. In other words the hydraulic resistance of piston 39 is at amaximum, as indicated by the point 81 in graph 82, the hydraulicresistance of piston 4| is at a minimum indicated by the point 88 ingraph 84, the resistance of piston 40 is substantially intermediate theminimum and maximum resistance possible as indicated by the point 89 ingraph 85; and similarly the resistance of the piston 42 is the same aspiston 40 as indicated by the point 90 in graph 86. If the referenceline 83` is considered to be the member 46, it will be seen that if thisline is moved in the receiver member.

8 direction of the arrow 9| corresponding to clock'-r wise movement ofthe member 46 such as to the position indicated by the dash and dot line92 that the resistance of piston 39 will decrease from the point 61y tothe point 93; the resistance-,of piston 4| will increase to the point94; the re-` sistance of piston 40 will decrease to the point 95, andthe resistance of piston 41 will increase to the point 96. Conversely,if the line 83 is moved in the direction of arrow 91, corresponding tothe counter-clockwise direction of member 46, the hydraulic resistanceof the various pistons will change in accordance with the graphs 98, 99,|08 and |0|. A second set of graphs |02, |03, |04 and |05 have beendrawn to represent the corresponding hydraulic resistance in the Sincethe transmitter `and receiver should always be in the same relativeposition, these graphs will be in the same phase relationship to thereference line |06 as the preceding set of graphs whereby the resistanceas indicated by the points |01, |08, |09 and ||0 will be equal to thepreceding resistances and should change in the same relationship. Therespective pairs of resistances have been connected by channels 62',63', 64' and 65 in accordance with Figure 17. It will now be seen thatwhen the resistance in to line 62' is equal to the resistance out of it,that the pressure in this line will be equal to one-half the mainpressure, and since the same is true with channel 63 it will be seenthat the pressure on opposite sides of the intermediatevpiston will bethe same and no movement will result. Also,

. the pressure on opposite sides of the piston ||2 intermediate lines64' and 65' will be the same and no movement will result.

If now the member 46 is rotated in a clockwise direction indicated bythe arrow 9|, there will be a momentary unbalancing of the pressure inthe various channels due to the fact that the resistance in in all ofthese channels is now different from the resistance ou of them. In otherwords, the pressure P1 in channel 62 has decreased which will be evidentfrom equation 9,

because the resistance 11 will now be less and therefore P1 will be asmaller fraction of the pressure P than it was formerly. Similarly thepressure at P2 will be increased due to the increase in the value of theresistance 18. Since vthe pressure in channel 63 is now greater than thepressure in channel 62', there will be an unbalancing of the forcesacting on the piston 'and in such a direction as to cause clockwisemovement. Also, the pressure at l?3 in line 64' will be less than thepressure in channel 65 which again will act on the intermediate piston|12 to cause clock-wise movement. This clockwise movement is equivalentto movement ofthe reference line |06 to its dash and dot positionindicated by itsreference numeral |06'. When this position is reached,it will be seen that the resistances will now be equal to the incomingresistances and the opposing pressures and the pistons and I2 will againequalize, restraining any further movement and simultaneouslymaintaining the parts in a fixed position.

vThe pressure on opposite sides of the pistons and |12 diagrammaticallyrepresent the opposing pressures on the pair of pistons 39, 4| and onthe pair of pistons 42 and 40. It should now be clear that when thetransmitter member 46 is rotated either clockwise or counterclockwise,that differential pressures will now be set up in channels 62, 63, 64and 65 which will cause the '9 pistons in the receiver member to assumethe same position as those in the transmitter, or in other words be in`synchronous relation therewith.

One form of construction `by which the transmitter is interconnectedwith the receiver is shown in Figures 2 and 3, the transmitter beingshown in Figure 3 and the receiver or gun being shown in Figure 2. I-nFigure 3 the hydraulic transmitter H3` is fixed with the column andprovided with a bevel gear H4 on one end of a shaft |I5 which isdirectly connected to the cam member 46. A large bevel gear ||6 which isin the ratio of 6 to 1 to the bevel gear ||4 meshes therewith wherebyone rotation of the gear ||6 will eifect six rotations of the cam 4G. Asecond bevel gear I1 is integral with gear ||6 and both are mounted vforfree rotation on the shaft |I8 carried by the column H. The gear II1meshes with the bevel gear 9 keyed to the end of pivot pin 23 which ismounted for free rotation in the support 24 but is keyed with thesupport 2| which carries the sights 2'2.

The hydraulic transmitter ||3 is connected by four individual channels|28, |2|, |22 and |23 to the hydraulic receiver member |24 which, asshown in Figure 6, is mounted in one end of a housing |25. The receivermember controls a motive power unit indicated generally by the referencenumeral |26 and which is coupled to the receiver in the manner of aservomotor. The output of this motive power unit is transmitted to shaft|21 having a worm gear |28 secured to the end thereof in mesh with aworm wheel |29 mounted for free rotation on the shaft |39. A bevel gear|3| is formed integral with the worm wheel and meshes with a similarbevel gear |32 which is keyed to one end of shaft |33, this shaft beingmounted for free rotation on the subsupport I5 but keyed at its upperend to the gun support I I. It should now be evident that when the sightsupport 2| is rotated in the plane of the upper surface of thesub-support 24 regardless of the angle of this plane, that the hydraulictransmitter will be rotated through the intermediate gearing to adefinite position thereby disturbing the existing pressuresin channels|20 to |23 inclusive which will cause a corresponding movement from thereceiver |24 until those pressures have been equalized again, and whenthis equalization occurs the receiver will be in the same relativeposition as the transmitter. This rotation of the receiver will cause aprede.- termined movement o-f the servomotor |26 and thereby rotation ofthe gun support to a. position parallel to the position of the sightingvsup- The sub-support 24 has a bevel gear |34 secured thereto whichmeshes in six to one ratio with a bevel gear |35 secured to the end of ashaft. |36 of a second hydraulic transmitter |31. This transmitter isconnected by lines |38, |39, |40 and |4| to a receiver |42 whichoperates in turn a motive power unit |43 connected through worm |44 andworm wheel |45 to the sub-support l5.

Y The motive power unit |26 is coupled to the receiver in a ratio of oneto six so that one rotation of the receiver |24 will effect sixrevolutions of the shaft |21. Also the ratio of the worm |28 to the wormwheel |29 is 36 to 1 so that it will .take 36 revolutions of the worm toeffect one rotation of the worm wheel. These two trains thus make-itpossible for any movement of the Agu-n sights about the pivot 23 orabout the pivot II'8 to 4be vimmediately transmitted to the gun supportvI I and correspondingly position it about the pivots 3 and |39 parallelto the axis of the sights carried by the support 2|. The construction'shown in Figures 2 and 3 requires a flexible hydraulic connectionbetween the transmitter and receiver due to the fact that thetransmitters are carried by the support Ill which is also rotatableaboutthe ,pivot I8 while the receiving elements are carried by the support I|which is rotatable about the pivot 21.

The .details 4of this flexible connection are shown in Figures 7 and 8and comprise a tapered plug .|46 carried by lthe base 20 rotatably ttingin a tapered bore formed in the housing |41 which is carried by thestandard I B- and rotatable therewith. This plug has four annulargrooves |29', |2I., |22' and |23 to which the channels |120 to .|23inclusive are connected, and a second group of four annular grooves|38', |39', |48' and I 4| to which the channels I 38 to |4| inclusiveare connected. Each one of these connections may be made as shown inFigure 8, the respective pipes being connected by a nipple |48 threadedin a bore .|49 formed in the member |41. These connections will beequally spaced about the outside periphery of the member |41 as .moreparticularly shown in Figure 1. Each annular groove is connected by aradial hole |50 to a longitudinally extending hole such .as |5|. Theselongitudinal holes terminate at the bottom of the member |46 into whichthe respective continuations of the various channels are threaded asmore particularly shown at I 5?v in Figure 8. It will now be seen' thatthe vertical standard |10 may be rotated relative to the base member 2|!without disturbing the hydraulicv connection in these variouschannels.`The member |46 has an additional annular groove |53 to which uidpressure is supplied from a pump |54 driven by a suitable prime mover,such as a motor |55 which may be either an electric motor or an internalcombustion engine if the device is used in the field remote from asource of electrical energy. The annular groove |53 is connected by thepipe 48 to the passage 41 in the transmitter as shown in Figure 11 tosupply the fluid pressure thereto.

1 Since the flexible hydraulic connection increases the possible leakagefrom the system, it is preferable to use the arrangement shown inFigures 4 and 5 which eliminatesthe use of this connection, Inv Figure 5thetransmitter ||3 for the rotary movementv of support 24 is carried bya bracket |56 which is integral with the base 20. The transmitter 31 isconnected by a pair of spur gears l|51 and |58 'in va one to one ratioto a vertical shaftl59, this shaft being connected by bevel gearsA |60in a one to one ratioto the horizontal shaft |6|. This shaft hasintegrally secured thereto a bevel pinion |62 meshing with bevel gear|63 in a six to one ratio whereby one rotation of gear |63 will effectsix revolutions in the gear |62. The gear |63 is keyed to one end of thepinion 23 which is xed at the, upper end of the support 2|.

The transmitter H3 is connected by a spur gear train comprising gears|64, |65 and |66 in a one to one ratio to shaft |61. This shaft carrieson its upper end ak bevel pinion |68 meshing with the bevel gear |69 xedto the support 24.

The transmitter 3 is vconnected by the hydraulic cable'fIThaving fourlindividual lines inclosed therein-'to the receiver |24' in the samemanner asbefor'e, thefre'ceiver in turn controls "put shaft |21 of themotor.

11 the movement of the servomotor |26 in the same manner as before. Theoutput shaft |21 of this servomotor is connected, however, by spur gearI1I to gear |12 in a three to one ratio the gear |12 having integraltherewith a pinion |13 meshing with a gear |14 in a two to one ratio,the gear |14 being carried by the vertical shaft |15. By means of thisgearing, one rotation of the shaft |21 will effect one-sixth of arevolution in the shaft |15. This shaft is connected by worm and wormwheel connection |16 to the support I5, the worm and worm wheel having areduction ratio of one to six. The transmitter |31 is connected by thecable |16' to the receiver I42-which ,controls the operation of theservomotor |43 .as in the construction shown in Figure 2, but thevservomotor is connected bya spur gear |11 to a gear |18 secured to theend of shaft |19 in a one to six ratio whereby one rotation of gear I 11will effect one-sixth of a revolution in the shaft |19. This shaft isconnected at the upper end by bevel gearing |80 in a one to one ratio toshaft `I 8 I This shaft has fixed thereto a spiral gear |82 meshing withaV spiral gear |83 in a one to six ratio, the latter gear being keyed tothe end of the shaft I3 which is fixed with the gun support I I. Anadditional transmitter and receiver have been provided for the rotarymovement of the vertical support II when rotated by means of the handle3|. This handle has a spring pressed grip |84 pivotally mounted thereonfor friction- `ally engaging a flange |85 fixed with the support 28 forholding the standard I'I in any adjusted position. The lower end of thesupport I I .is therefore provided with a large spur gear |86 xed forrotation therewith and meshing with .the pinion gear |81 fixed to theend of the shaft .|88 of the hydraulic transmitter |89. The ratio ofthis gearing is six to one whereby one rotation of the part II willeffect six revolutions of the transmitter |89. This transmitter isconnected by-the cable |90 to the hydraulic receiver `I9I which has theservomotor as in the previous constructions, the servomotor beingconnected to a worm |92 meshing with a worm wheel |93 in a 36 to oneratio, the worm wheel being carried by the lower end of the gun supportI0.

The motive power unit includes an hydraulic motor more particularlyshown in Figures 6 and with a port 206 and in order to obtain maximumguidance and minimum length of piston the opposite end of the pistonfrom the roller is valso provided with a skirt 201 having longi- 'spacedplanes.

ures 6 and I5, each port 206 is connected by a' radial passage 2|4 to aport 2|5. The shaft |21 has a pair of longitudinal passages 2| 6 and 2|1formed therein which terminate in radial bores 2I8 and 2I9 which, asshown in Figure 6, lie in For instance, as shown in Figure l5, thepassage 2 I 1 terminates in three radial bores 2| 9, 220 and 22| lyingin one plane and the passage 2I6 terminates in three radial pas-J sages2 I8, 222 and223 lying in a different plane. It will also be observedfrom Figure 15 that these six radial passages are equally angularlypositioned about the center of the shaft |21, even although they lie indifferent planes. Each radial passage, however, terminates in an arcuateslot as shown at 224 in Figure 6 whereby all of these radial passagesare adapted to cooperate with all of the motor ports 2|5 in propersuccession. For instance, if the channel 2I6 is connected to a source ofpressure, the pressure Will flow through radial passage 2I8 to piston I99 which, it will be noted, acts on the lobe 2|| to cause ton. 'I'heupper end of each cylinder is provided u tudinal slots 208 formedtherein, one of the slots being opposite the port 206 to maintaincommunication between the port and the cylinder in all axial positionsof the piston and the other lslot receiving a pin 209 to preventrotation of .the piston in the cylinder and thereby maintaining theroller 200 in its proper plane relative to the control cam 2I0. This camhas three lobes ,2| I, 2 |.2 and 2|3. These lobes are equally spaced andso arranged that itis acted upon successivelybythe pistons to causerotation ,of the out` As shown in Figcounterclockwise rotation of theshaft 2|1 due to the fact that the point of contact 225 acts in offsetrelation to the center 226 of the shaft `I21. When the channel 2 6 isunder pressure the channel 2 I1 is connected to exhaust and this permitsthe fluid acting on piston in cylinder |91 to exhaust and permit outwardmovement of the piston. As this rotation continues slightly beyond theposition shown in Figures 13 and 16, the radial pressure channel 223will be connected to supply pressure to cylinder |96 thereby causinginward movement of the contained piston and the radial exhaust lpassage220 will be connected to cylinder |98 permitting the same to moveoutward. This sequence will continue, thereby causing continuousrotation of shaft 21 so long as pressure is supplied to channel 2 I 6and channel 2 I1 is connected to exhaust. If the connections arereversed to these two channels so that channel 2I1 is a pressure channeland 2I6 an exhaust channel, the direction of rotation of shaft |21 willbe reversed. Further, if all flow is cut oil. from these two channelsthe motor will stop.

The flow to these two channels is controlled by a Valve mechanism moreparticularly shown in Figures 6 and l2. As shown in Figure 6, thechannel 2|6 is connected by a'radial port 221 to an annular groove 228formed in the valve hous` ing 229 which is mounted for free rotationabout the shaft |21. The channel 2I1 is connected by a radial port 230to an annular groove 23| formed in the valve housing. The annular groove228 is connected by the passage 232 to the annular groove 233 formed inthe valve sleeve 234, this groove having radially extending passages 235communicating with the interior of the valve sleeve. The annular groove23|' is connected by the passage 236 to the annular groove 231 formed inthe valve sleeve and having radial ports 238 formed in the bottomthereof communicating with the interior of the sleeve. A valve plunger239 is reciprocably mounted in the sleeve and has a spool 240 ofsufficient width to close the pressure port 24| when in a centralposition, and a pair of end spools 242 and 243 which normally close theexhaust ports 244 and 245. Fluid pressure is. delivered to the devicethrough channel 246 which, as shown in Figure 16, communicates by radialpassage 241 tothe annular groove 248 formed inthe sleeve 249. The sleeve249 has a'plurality of radialholes 250 formed in the bottom of groove248l communirating with an annular groove 25| formed-in the periphery ofshaft |21. A radial bore 252 in the bottom of this groove communicates'with the longitudinal passages 253 formed in the shaft and terminating,as shown in Figure 12, in a similar radial passage 253 through which theiiuid is supplied to the annular groove 254 formed in the Valve housing229 and connected with port 245. The two exhaust ports 244 'and '245 areconnected by passages 255 and 25e to thev remaining annular groove 251formed in the valve body which, in turn, is connected by radial pas-'sage 258 to the longitudinal bore 259. This bore communicates as shownin Figure 16, with a similar annular groove 260 to which the exhaustpipe 26| is connected. It will now be seen that fluid Apressure issupplied to the p-ressure port 24| and thisJ port is selectivelyconnected to either passage 2HE or 2|1 by the spool 24% carried by thevalve plunger v239. y

This valve plunger has a slot 282 formed in the end thereof forreceiving a ball-ended bell crank 263 pivotally mounted at 284 in thevalve housing I229. The other arm 265 of this bell crank has abifurcated slot 266 in which ts a f pin 281 carried by, as shown inFigure 14, a rotatable plate 268 fixed as shown in Figure 6, to the camplate 45. It will now be apparent that as the cam plate 4K5 of thereceiver member is rotated, it will act through the plate 258 and pins269 to oscillate the bell crank 263 vand move Athe valve plunger inap-redetermineddirection to connect the pressure port 24| to eitherpassage 2|'6 or 2|1 and thereby cause actuation of the motor kwhich inturn will cause clockwiseor counter-clockwise rotation of the outputshaft '239 so as to centralize the spool 240 with'respect f 4to thepressure port 2M. As previously mentioned,` the motor operates in a sixto one ratio with respect'to the receiver and therefore the feed backmechanism must be of such construction as to permit six times theangular movement of receiver member Se in the shaft |21 beforeterminating the movement thereof. To this end the shaft |21 is providedwith a pinion gear 210 on the end thereof meshing with the spur gear 21|which is journaled on a shaft 212 carried by the valve housing 229 formovement therewith. The gear 21| meshes with. an internal gear 213which, as shown in Figure 6, is fixed with the outside housing of themotive power unit. This gearing 'is in such a ratio that as the shaft2|1 rotates, it will cause the gear 21| to travel with respect to thefixed internal gear N3 and cause rotation of the valve housing 229 aboutthe axis of shaft |21 .and in a direction to follow up the movement ofthe valve plunger 239 caused by rotation of plate 258. f

There has thus `been provided an improved mechanism for transmittingmotion from a moyable object, such as the sighting element of a vfirecontrol system for anti-aircraft defense weapons, to the weapon itself,including pairs of interconnected hydraulic synchronous devices wherebymovement of one causes a synchronized movement of the other, togetherwith a power arnplifying means consisting of a servo-motor consitotrolled by' the 1 receiver 'synchronous device, whereby the large torquenecessary to move the gun will be produced by the yservo-motor and onlya-small torque willbe necessary to transmit the motion from thetransmitter to the receiver.

What is claimed is:

l. In a signaling system, the combination of arotatable transmitter, aremotely located rotatable receiver, a plurality of Aopposed pairs offluid operable devices connected in couple formation to the receiver, asource of pressure fluid, means conducting the uid for continuous flowto and from said devices, resistance means in the iow from said devicesfor vcontrolling the individual pressures thereon, additional resistancemeans in the flow to said devices forvarying the pressures as`determined by the first-named resistances,

means for rotating the receiver, means responsive to rotation of thetransmitter for complementally varying one set of resistances andthereby inversely varying the pressures on the opposed devices lto causerotation of the receiver, and means responsive to receiver rotation forcomplementally varying the other `set of resistances to equalize theopposed pressures on said devices.

2. In a signaling system, the combination of a rotatable transmitter, aremote rotatable receiver, a plurality `of opposed pairs of fluidoperable devices connected in couple formation to the re-l ceiver, asource o'f pressure operating fluid, a. multiple channel connection fordelivering fluid from said source tothe 'individual devices, means intheindividual channels for variably resisting the ow from said devices andthereby controlling the pressure thereon, `additional means in theindividual channels for variably resisting the vflow to said devices,means for rotating the receiver, means responsive to rotation of thetransmitter for varying the last-named resistances to vary the pressuresAacting on said devices and thereby cause rotation of the receiver, andmeans responsive to rotation of the receiver upon movement through anangle equal to the angle of rotation of the transmitter for equalizingthe pressure on said devices to stop the receiver.

3. In a gun control mechanism, the combination of a transmitter having arotatable portion, a sighting apparatus operatively connected to therotatable portion of the transmitter for rotation thereof: upon movementof the sighting apparatus through la given plane, a gun movable in a4plane coincident with the plane of movement of thesighting apparatus, areceiver having a rotatableportion to move the gun, a servo-motoroperatively connecting the receiver to the gun, al plurality of pairs ofopposed fluid operable devices in the receiver, a source of pressurefor, delivering fluid continuously to said devices, means .on thetransmitter responsive Vto rotation of the rotatable portion of thetransmitter for rotating therotatable'portion of the receiver, saidmeans being responsive to rotation of the rotatable portion of thetransmitter forv inducing pressure changes in the'fluid acting on saiddevices to cause rotation of the rotatable portion of Vthe receiver, andmeans responsive to rotation of the rotatable portionfof the receiverfor equalizing said pressures when the receiver portion has movedthroughan angle equal to the movement of4 thetransmitter portion.v y

4. In a signaling system, the combination of a rotatable transmitter, varemotely located rotatable receiver, a plurality of pairs of opposedfiuid operable devices for connecting in couple formation to thereceiver to rotate it, a source of pressure operating fluid continuouslyflowing through said devices, means resisting the flow from said devicesto create an operating pressure thereon, additional means for resistingthe ilow to said devices, `said last-named means being located in thetransmitter, means responsive to the rotation of the transmitter througha predetermined arc to effect a predetermined change in the opposingpressures in each couple, and means responsive to rotation of vthemovable receiver through the same predetermined yarc to equalize theopposed pressures in each couple and to stop the receiver.

5. An hydraulic mechanism for maintaining a remotely located rotatablereceiver element in synchronized relation with a rotatable transmitterelement comprising a plurality of hydraulic channels, each channelcontaining a first resistance, a piston, and a second resistance in theorder named, a common source of pressure for maintaining a continuousflow through all of said channels, said pistons being mounted in thereceiver and arranged in couple formation, a multiple cam devicearranged in Contact with said pistons, the number of cams being odd innumber with respect to the number of said pistons, each cam having apiston advancing portion and a piston retracting portion whereby anequal pressure on opposed pairs of pistons will tend to hold the camdevice at rest, an increase in pressure on one piston over the other ofa couple will cause rotation of the cam in a clockwise direction, anincrease in pressure on the other piston will cause rotation in acounter-clockwise direction, and means in the transmitter for inducingpressure changes in the receiver to cause thereceiver to move insynchronized relation with the transmitter.

6. In a system for transmitting motion between spaced points, thecombination of a rotatable transmitter, a rotatable receiver, aplurality ofhydraulic channels extending from the transmitter to thereceiver, said receiver comprising four radial pistons arranged inopposing pairs, a rotatable cam member circumscribing the outer ends ofsaid pistons Yand having a plurality of arcuate-shaped cam portions oddin number with respect to the numbers of said pistons, means connectingsaid channels to the inner end of said pistons to cause outward movementthereof into contact with said cam portions, independent exhaustchannels connected to the respective plstons, resistance means in eachchannel variable in accordance with the position of the piston forcreating variable pressures thereon, said transmitter element beingsimilarly composed and including resistances for varying the pressure insaid channels whereby rotation of the transmitter will cause anunbalancing of pressure in the respective pairs of channels to causerotation of the. receiver7 which rotation will continue until theresistances in the receiver are made equal to the resistances in thetransmitter.

7. In a mechanism for transmitting motion between spaced points, thecombination of a rotatable transmitter, a rotatable follower, aplurality -of channels extending from the transmitter to Vthe follower,a source of pressure, means to cou- `ple the source of pressure to oneend of all of said channels to maintain a continuous flo-w therethrough,movable pistons associated with 16 both ends of all of said channels andsubject to the pressure therein, the pistons at one end being connectedin pairs to the transmitter, the pistons at the other end beingconnected in pairs to the follower, one member of each pair opposing thedirection of movement of the other member of said pair, whereby whenequal hydraulic pres'- sure exists in all of said channels said pistonswill be in equilibrium, means for rotating the follower, meansresponsive to movement of the pistons at the transmitter upon rotationof the transmitter to differentially vary the quantity of iiow in theseveral channels and thereby create differential pressures therein whichwill cause unbalance and resultant movement of the pis;- tons at thefollower and thus cause rotation of the follower, and means responsiveto movement of the last-named pistons to re-establish equal pressures insaid channels and thus terminate follower rotation.

8.' Means for maintaining a rotatable follower in synchronized relationwith a rotatable transmitter including a plurality of channels andextending from the transmitter to the follower, a source of pressure,means to couple the source of pressure to one end of all of saidchannels to maintain a continuous flow therethrough, mov,- able pistonsassociated with both ends of all of said channels and subject to thepressure therein, the pistons at one end being connected in pairs to thetransmitter, the pistons at the other end being connected in pairs tothe follower, one member of each pair opposing the direction ofAmovement of the other member of said pair, whereby when equal hydraulicpressure exists in all of said channels said pistons will beinequilibrium,

' and means for rotating the follower the lastnamed'means beingresponsive to movement of the pistons at the transmitter upon rotationof the transmitter to differentially vary the quantity of ow in theseveral channels and thereby create differential pressures therein whichwill cause unbalance and resultant movement of the pistons at thefollower and thus cause rotation of the follower, means responsive tomovement of the last-named pistons to reestablish equal pressures insaid channels and thus terminate follower 10- tation, and a servonnotormechanism operable by the follower for amplifying the output torquethereof.

HANSl ERNST.

BERNARD SASSEN.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS

